Driving type hydrostatic guideway assembly and grinding machine

Abstract

The utility model relates to a driving type static pressure guide rail assembly and a grinding machine. A driving type hydrostatic guideway assembly comprises a lathe bed, a workbench, an oil supply unit, a first one-way oil cylinder, a second one-way oil cylinder and an oil way system. Hydrostatic guideways are arranged on the surface of the lathe bed; the workbench is arranged on the hydrostatic guideway, and an oil film cavity is formed between the workbench and the hydrostatic guideway; the oil supply unit is arranged on the hydrostatic guide rail and used for filling hydrostatic oil into the oil film cavity. The first one-way oil cylinder is arranged on the surface of the lathe bed and is parallel to the length direction of the static pressure guide rail. The second one-way oil cylinder is arranged on the surface of the lathe bed, is parallel to the length direction of the hydrostatic guideway and is opposite to the first one-way oil cylinder in orientation; a first piston rod of the first one-way oil cylinder and a second piston rod of the second one-way oil cylinder are connected with the workbench; the oil way system communicates with the two first one-way oil cylinders, the second one-way oil cylinder and the oil supply unit.

Description

Technical Field

[0001] This application relates to the field of guideway grinding machine technology, and in particular to a drive-type hydrostatic guideway assembly and grinding machine. Background Technology

[0002] With the development of the precision machining industry, higher requirements are placed on the accuracy, stability, and service life of guideway grinding machines. Traditional mechanical guideways (such as sliding or rolling guideways) rely on solid contact, which are prone to wear after long-term use, leading to a decrease in accuracy and requiring frequent maintenance; single-point drive or single-cylinder structures are prone to off-center deformation under heavy load or high-speed conditions, affecting the quality of the machined surface; mechanical friction heat and vibration can be transmitted to the workpiece, causing irreversible errors in the machining of high-precision parts (such as optical components and semiconductor molds). Utility Model Content

[0003] Therefore, it is necessary to provide a driven hydrostatic guideway assembly and grinding machine to address the problems existing in traditional guideway grinding machines.

[0004] A drive-type hydrostatic guide rail assembly includes:

[0005] The bed is equipped with hydrostatic guide rails on its surface;

[0006] The worktable is set on the hydrostatic guide rail and has an oil film cavity between it and the hydrostatic guide rail;

[0007] The oil supply unit, mounted on the hydrostatic guide rail, is used to fill the oil film cavity with hydrostatic oil.

[0008] The first one-way hydraulic cylinder is mounted on the surface of the bed and is set parallel to the length direction of the hydrostatic guide rail;

[0009] The second one-way cylinder is installed on the surface of the bed, parallel to the length direction of the hydrostatic guide rail, and opposite to the orientation of the first one-way cylinder; the first piston rod of the first one-way cylinder and the second piston rod of the second one-way cylinder are both connected to the worktable.

[0010] The oil circuit system is connected to the first one-way cylinder, the second one-way cylinder, and the oil supply unit, respectively.

[0011] In one embodiment, the oil circuit system includes a first oil tank and a reversing valve;

[0012] The first one-way cylinder includes a first oil inlet and a first oil return port connected to the first oil tank. When hydraulic oil is filled into the first oil inlet, the first piston rod extends relative to the first one-way cylinder.

[0013] The second one-way cylinder includes a second oil inlet and a second oil return port connected to the first oil tank. When hydraulic oil is filled into the second oil inlet, the second piston rod extends relative to the second one-way cylinder.

[0014] The reversing valve is configured on the common connecting passage between the first oil inlet, the second oil inlet, and the first oil tank.

[0015] In one embodiment, the oil circuit system includes a second oil tank and a hydrostatic oil pipeline, the second oil tank being connected to all oil supply units via the hydrostatic oil pipeline.

[0016] In one embodiment, the oil supply units are evenly arranged along the length of the hydrostatic guide rail, and the oil supply units are provided with an oil supply port facing the oil film cavity and a connecting oil port for connecting to the hydrostatic oil pipeline.

[0017] In one embodiment, the hydrostatic guide rails are respectively configured as a V-shaped recessed guide rail and a flat guide rail, and the worktable is slidably connected to the V-shaped recessed guide rail and the flat guide rail simultaneously via a slider provided at the bottom;

[0018] The oil supply units are evenly distributed inside the V-shaped recessed guide rail and the flat guide rail.

[0019] In one embodiment, it further includes: a cable chain, one end of which is connected to the bed and the other end of which is connected to the worktable;

[0020] The hydrostatic oil pipeline is mounted on the cable chain.

[0021] In one embodiment, an integrated pressure sensing system is also included, comprising a first pressure sensor and a second pressure sensor connected to the oil circuit system.

[0022] The first pressure sensor is disposed in the oil film cavity formed by the V-shaped concave guide rail and the worktable; the second pressure sensor is disposed in the oil film cavity formed by the planar guide rail and the worktable.

[0023] In one embodiment, a first flow control valve is disposed between the first oil tank and the first oil inlet;

[0024] A second flow control valve is installed between the first oil tank and the second oil inlet;

[0025] A third flow control valve and a static pressure valve are installed between the second oil tank and the oil supply unit.

[0026] In one embodiment, the second oil tank is connected to each oil supply unit via a rigid diversion pipe.

[0027] A grinding machine comprising a drive hydrostatic guideway assembly according to any of the above.

[0028] The aforementioned driven hydrostatic guideway assembly includes: a bed, a worktable, an oil supply unit, a first one-way cylinder, a second one-way cylinder, and an oil circuit system. A hydrostatic guideway is provided on the surface of the bed; the worktable is mounted on the hydrostatic guideway, with an oil film cavity between it and the guideway; the oil supply unit is mounted on the hydrostatic guideway and is used to fill the oil film cavity with hydrostatic oil. The first one-way cylinder is mounted on the surface of the bed and is arranged parallel to the length direction of the hydrostatic guideway. The second one-way cylinder is mounted on the surface of the bed, parallel to the length direction of the hydrostatic guideway, and faces in the opposite direction to the first one-way cylinder; the first piston rod of the first one-way cylinder and the second piston rod of the second one-way cylinder are both connected to the worktable; the oil circuit system is connected to the two first one-way cylinders, the second one-way cylinder, and the oil supply unit. The worktable and the bed are completely isolated by the hydrostatic oil film in the oil film cavity, completely eliminating dry friction, stick-slip effect, and wear problems. Meanwhile, the opposing dual-cylinder linkage design eliminates mechanical transmission gaps through dynamic balancing of cylinder thrust, further suppressing motion vibration and improving displacement accuracy under low-speed conditions.

[0029] A grinding machine that has the aforementioned beneficial effects. Attached Figure Description

[0030] Figure 1 This is a top view of the drive hydrostatic guide rail assembly provided in an embodiment of this application.

[0031] Figure 2 This is a schematic diagram of the oil circuit connection of the drive hydrostatic guide rail assembly provided in the embodiments of this application.

[0032] Figure 3 This is a cross-sectional view of the drive hydrostatic guide rail assembly provided in an embodiment of this application.

[0033] Figure 4 This is a schematic diagram of the structure and fit of the oil supply unit provided in the embodiment of this application on the V-shaped recessed guide rail.

[0034] Figure 5 This is a partial structural schematic diagram of the drive-type hydrostatic guide rail assembly provided in an embodiment of this application.

[0035] Figure 6 This is a partial connection diagram of the oil circuit system provided in an embodiment of this application.

[0036] Figure 7 This is a schematic diagram showing the connection between the third flow control valve and the static pressure guide rail provided in an embodiment of this application.

[0037] Figure 8 This is a top view of the drive hydrostatic guide rail assembly hidden behind the worktable, as provided in the embodiments of this application.

[0038] Figure 9 for Figure 8A magnified view of a portion of point A in the middle.

[0039] Icon labels:

[0040] 1000. Bed; 1001. Hydrostatic guide rail; 1002. V-shaped recessed guide rail; 1003. Flat guide rail;

[0041] 2000, Workbench;

[0042] 3000, Oil supply unit; 3001, Oil supply port; 3002, Connecting oil port;

[0043] 4000, First one-way hydraulic cylinder; 4001, First oil inlet; 4002, First oil return port;

[0044] 5000, Second one-way hydraulic cylinder; 5001, Second oil inlet; 5002, Second oil return port;

[0045] 6000, Oil circuit system; 6010, First oil tank; 6011, Directional control valve; 6020, Second oil tank; 6021, Static pressure oil pipeline; 6030, First flow control valve; 6031, Second flow control valve; 6032, Third flow control valve; 6033, Static pressure valve;

[0046] 7000, First pressure sensor; 7001, Second pressure sensor;

[0047] 8000, cable chain. Detailed Implementation

[0048] To make the above-mentioned objectives, features, and advantages of this application more apparent and understandable, the specific embodiments of this application are described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of this application. However, this application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of this application. Therefore, this application is not limited to the specific embodiments disclosed below.

[0049] In the description of this application, it should be understood that if terms such as "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" appear, these terms indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0050] Furthermore, where the terms "first" and "second" appear, these terms are for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this application, where the term "multiple" appears, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0051] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0052] In this application, unless otherwise expressly specified and limited, the use of descriptions such as "above" or "below" the second feature indicates that the first and second features are in direct contact or indirect contact via an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. Similarly, "below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0053] It should be noted that if an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. If an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. If so, the terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used in this application are for illustrative purposes only and do not represent the only possible implementation.

[0054] See Figures 1-5 As shown, Figure 1 This is a top view of the drive hydrostatic guide rail assembly provided in the embodiments of this application. Figure 2 This is a schematic diagram of the oil circuit connection of the drive hydrostatic guide rail assembly provided in the embodiments of this application. Figure 3 A cross-sectional view of the drive hydrostatic guide rail assembly provided in the embodiments of this application. Figure 4This is a schematic diagram of the structural fit of the oil supply unit on the V-shaped recessed guide rail provided in the embodiments of this application. Figure 5 This is a partial structural diagram of the driven hydrostatic guide rail assembly provided in an embodiment of this application. The driven hydrostatic guide rail assembly includes: a bed 1000, a worktable 2000, an oil supply unit 3000, a first one-way cylinder 4000, a second one-way cylinder 5000, and an oil circuit system 6000. A hydrostatic guide rail 1001 is disposed on the surface of the bed 1000, and the worktable 2000 is disposed on the hydrostatic guide rail 1001, with an oil film cavity between the worktable 2000 and the hydrostatic guide rail 1001. The oil supply unit 3000 is disposed on the hydrostatic guide rail 1001 and is used to fill the oil film cavity with hydrostatic oil. The first one-way cylinder 4000 is disposed on the bed 1000 and is arranged parallel to the length direction of the hydrostatic guide rail 1001. A second one-way hydraulic cylinder 5000 is mounted on the bed 1000. The second one-way hydraulic cylinder 5000 is parallel to the length of the hydrostatic guide rail 1001, and its orientation is opposite to that of the first one-way hydraulic cylinder 4000. The first piston rod of the first one-way hydraulic cylinder 4000 and the second piston rod of the second one-way hydraulic cylinder 5000 are both connected to the worktable 2000. The hydraulic system 6000 is connected to the first one-way hydraulic cylinder 4000, the second one-way hydraulic cylinder 5000, and the oil supply unit 3000, respectively. When the hydraulic system 6000 supplies oil to either the first one-way hydraulic cylinder 4000 or the second one-way hydraulic cylinder 5000, the piston rod of one cylinder extends, while the piston rod of the other cylinder retracts, thereby causing the worktable 2000 to move in one direction.

[0055] The first piston rod and the second piston rod are not shown in the figure. The specific structure of the first one-way cylinder 4000 and the aforementioned second one-way cylinder 5000 can be referred to the telescopic cylinder with piston rods.

[0056] The static pressure oil film eliminates friction. The uniform hydraulic oil within the nonlinear oil film cavity forms a stable static pressure support, completely isolating the worktable 2000 from the bed 1000, eliminating the low-speed crawling phenomenon caused by dry friction in traditional sliding guides, and ensuring smooth movement. The dual-cylinder reverse linkage design of the first unidirectional cylinder 4000 and the aforementioned second unidirectional cylinder 5000 (when one side supplies oil for propulsion, the other side actively retracts) eliminates mechanical transmission gaps through dynamic balance of cylinder thrust, further suppressing motion vibration and improving displacement accuracy under low-speed conditions.

[0057] In some embodiments of this application, the hydraulic system 6000 includes a first oil tank 6010 and a directional valve 6011. The first one-way cylinder 4000 is provided with a first oil inlet 4001 and a first oil return port 4002 communicating with the first oil tank 6010. When hydraulic oil is filled into the first oil inlet 4001, the first piston rod extends relative to the first one-way cylinder 4000.

[0058] The aforementioned second one-way cylinder 5000 is provided with a second oil inlet 5001 and a second oil return port 5002 communicating with the first oil tank 6010. When hydraulic oil is filled into the second oil inlet 5001, the second piston rod extends relative to the second one-way cylinder 5000. The aforementioned reversing valve 6011 is configured on the common communication passage of the first oil inlet 4001, the second oil inlet 5001, and the first oil tank 6010, and is used to control the flow direction of the hydraulic oil.

[0059] The first oil tank 6010 serves as the storage and supply center for hydraulic oil, and is connected to the first oil inlet 4001 and the first oil return port 4002 of the first one-way cylinder 4000, and the second oil inlet 5001 and the second oil return port 5002 of the second one-way cylinder 5000 via pipelines.

[0060] The reversing valve 6011 is connected in series on the common pipeline between the first oil tank 6010 and the first oil inlet 4001 and the second oil inlet 5001. By switching the position of the valve core, the hydraulic oil is controlled to flow to the first oil inlet 4001 or the second oil inlet 5001, while the return oil passage of the oil cylinder on the other side is opened.

[0061] During forward motion, the reversing valve 6011 switches to the first oil inlet 4001 open state, and hydraulic oil flows from the first oil tank 6010 into the first oil inlet 4001 through the reversing valve 6011. The first oil inlet 4001 is connected to the rodless chamber of the first one-way cylinder 4000, pushing the first piston rod to extend. At the same time, the second return port 5002 of the second one-way cylinder 5000 is connected to the oil tank, and the second piston rod is passively retracted under mechanical linkage with the worktable 2000.

[0062] During reverse movement, the reversing valve 6011 switches to the second oil inlet 5001 open state, and hydraulic oil flows into the second oil inlet 5001. The second oil inlet 5001 is connected to the rodless chamber of the second one-way cylinder 5000, pushing the second piston rod to extend. At the same time, the first return port 4002 of the first one-way cylinder 4000 is connected to the oil tank, and the first piston rod is passively retracted.

[0063] The oil inlet and outlet ports of the dual oil cylinders need to be arranged symmetrically to ensure that the oil circuit length and pipe diameter are consistent and to reduce pressure loss differences.

[0064] The 6011 reversing valve can be a two-position four-way valve or a three-position four-way valve, and can achieve automatic reversing through electromagnetic or hydraulic control to meet the automation requirements of the 2000-degree forward and reverse movement of the worktable.

[0065] By switching the oil circuit using the directional valve 6011, the alternating oil supply of the two oil cylinders can be achieved, which can drive the worktable 2000 to move forward and backward without an additional power source, simplifying the complexity of the control system and improving the level of automation.

[0066] When one side of the hydraulic cylinder extends the piston rod by receiving oil, the other side of the hydraulic cylinder passively contracts through the return oil passage. By using the opposing forces of the two hydraulic cylinders (such as the first piston rod pushing and the second piston rod pulling), the gaps in the mechanical transmission chain (such as the lead screw backlash) are forcibly offset, preventing the worktable 2000 from experiencing displacement lag or vibration due to the presence of gaps. This significantly improves motion accuracy, especially during low-speed reversing.

[0067] The symmetrical oil circuit design shortens the flow path of hydraulic oil from the oil tank to the two cylinders, reducing pressure fluctuations and oil compression delays. This allows the directional valve 6011 to move quickly and synchronously with the cylinder movement, improving system response speed. The shared first oil tank 6010 avoids the oil balance problem associated with dual tanks. The oil tank's buffering effect reduces vibrations caused by oil impacts, enhancing smoothness of movement.

[0068] The unidirectional hydraulic cylinder only bears hydraulic thrust in one direction, while the other side is reset by mechanical linkage. This reduces bidirectional wear on the cylinder seals (traditional bidirectional hydraulic cylinders must withstand bidirectional pressure) and extends the life of the seals. In the non-working state, neither cylinder bears hydraulic load, allowing the hydraulic system to operate at low pressure, reducing energy consumption.

[0069] Through the coordinated control of the directional valve 6011 and the dual one-way cylinders, the hydraulic system 6000 realizes the automated drive, gap elimination and precise reversal of the bidirectional movement of the worktable 2000. At the same time, the symmetrical hydraulic circuit design improves the response speed and stability, making it suitable for precision mechanical equipment with extremely high requirements for low-speed precision and reliability.

[0070] In some embodiments of this application, under the above-mentioned conditions, the oil circuit system includes a second oil tank 6020 and a static pressure oil pipeline 6021; the second oil tank 6020 serves as a storage container for static pressure oil, and the static pressure oil pipeline 6021 connects the second oil tank 6020 to all oil supply units 3000 (oil chamber supply points set on the static pressure guide rail 1001) to form a closed circulation system.

[0071] The main oil pipe extends from the second oil tank 6020, passing through components such as a filter, oil pump, and pressure regulating valve, before branching into multiple parallel hydrostatic oil branches. Each branch corresponds to one or more oil supply units 3000. Each hydrostatic oil branch is connected to the oil chamber inlet of the oil supply unit 3000 via a throttle (such as a capillary tube or a slit throttle) to ensure pressure balance in each oil chamber. Oil overflowing from the oil film chamber returns to the second oil tank 6020 through the return oil pipe, forming a closed-loop circulation.

[0072] To achieve the oil supply function, the oil circuit system 6000 can also be equipped with supporting structures based on existing technologies, such as oil pumps, filters, temperature control systems, and pressure sensors. Through the centralized layout of the second oil tank 6020 and the static pressure oil pipeline 6021, the oil circuit system 6000 achieves uniform and stable oil supply to each oil chamber of the static pressure guide rail 1001, offering significant advantages in improving motion accuracy, reducing wear, lowering energy consumption, and reducing maintenance costs.

[0073] In some embodiments of this application, the oil supply units 3000 are evenly arranged along the length of the hydrostatic guide rail 1001. Each oil supply unit 3000 is provided with an oil supply port 3001 facing the oil film cavity and a connecting port 3002 for connecting to the hydrostatic oil pipeline 6021. The oil supply units 3000 are arranged at equal intervals along the length of the hydrostatic guide rail 1001, and the interval is calculated and determined based on the guide rail length, load distribution, and oil film stiffness requirements.

[0074] In the width direction of the guide rail, the oil supply units 3000 are arranged in a matrix (such as a double or four-row layout) to ensure that the oil film pressure evenly covers the bottom surface of the worktable 2000.

[0075] The oil inlet 3001 is directly facing the oil film cavity, and a conical flare or throttling groove can be designed at the outlet to control the oil outlet direction and flow rate, and avoid jet impact on the stability of the oil film.

[0076] The connecting oil port 3002 is connected to a branch of the hydrostatic oil pipeline 6021 via threads or flanges. A sealing ring is installed at the interface or it is fixed by welding to ensure no leakage.

[0077] The internal flow channel oil supply unit 3000 is designed with damping holes or slotted throttles to ensure that the static pressure oil entering from the connecting oil port 3002 is evenly diffused to the oil supply port 3001, reducing pressure fluctuations.

[0078] The uniform arrangement along the length of the guide rail ensures that the oil film pressure is continuous and consistent on the bottom surface of the worktable 2000, eliminating the tilting or deformation of the worktable 2000 caused by uneven support, and improving the machining or measurement accuracy.

[0079] Each oil supply unit 3000 receives static pressure oil synchronously, ensuring that the worktable 2000 starts or stops without local lag or vibration, especially maintaining smooth movement during high-speed reversals. The matrix-distributed oil supply units 3000 make the system more tolerant to off-center loads. When the worktable 2000 is subjected to force on one side, the local oil chamber pressure automatically increases (through flow regulation via a throttle), maintaining overall oil film stability and preventing contact wear at the guide rail edges.

[0080] This design achieves uniform distribution of oil film support force and consistent dynamic response of hydrostatic guide rail 1001 through the uniform arrangement of oil supply units 3000 and reasonable oil port configuration. It has significant advantages in improving motion accuracy, anti-eccentric load capacity and maintenance convenience, and provides a reliable basic component solution for high-precision equipment.

[0081] In some embodiments of this application, the hydrostatic guide rail 1001 is configured as a V-shaped recessed guide rail 1002 and a flat guide rail 1003, respectively. The worktable 2000 is slidably connected to both the V-shaped recessed guide rail 1002 and the flat guide rail 1003 via a slider located at its bottom. The oil supply unit 3000 is evenly distributed inside the V-shaped recessed guide rail 1002 and the flat guide rail 1003. The V-shaped recessed guide rail 1002 has symmetrical V-shaped grooves machined on the surface of the bed 1000 to provide radial positioning constraints and withstand lateral forces and torques. The flat guide rail 1003 is arranged parallel to the V-shaped recessed guide rail 1002 and serves as the main support surface, bearing vertical loads. The bottom of the slider structure worktable 2000 is correspondingly configured with a V-shaped slider and a flat slider. The V-shaped slider is embedded in the V-shaped recessed guide rail 1002, and the flat slider is in contact with the flat guide rail 1003. Oil supply units 3000 are evenly distributed on the two inclined surfaces of the V-groove, with the oil inlets facing the V-shaped contact surface of the slider. The oil supply units 3000 are distributed in a matrix on the surface of the planar guide rail 1003, covering the entire bottom surface of the slider.

[0082] The oil supply unit 3000 of the V-shaped recessed guide rail 1002 and the flat guide rail 1003 is connected to the static pressure oil pipeline 6021 through a parallel branch to ensure pressure balance.

[0083] The oil film of the V-shaped recessed guide rail 1002 provides lateral positioning stiffness to prevent the worktable 2000 from shifting horizontally; the oil film of the flat guide rail 1003 provides vertical support stiffness to support the weight of the worktable 2000 and the workpiece.

[0084] The self-centering function of the V-shaped recessed guide rail 1002 eliminates lateral clearance and, in conjunction with the planar guide rail 1003, achieves "automatic centering," which is superior to a single planar guide rail 1003 or a double V-shaped recessed guide rail 1002 layout.

[0085] The oil film on both guide rails works simultaneously to suppress the influence of micro-unevenness on the guide rail surface on the motion. There is no crawling phenomenon under high-speed or low-speed conditions, and the smoothness of the motion reaches the nanometer level.

[0086] The uniform distribution of the oil film prevents direct contact between the slider and the guide rail. The V-shaped and flat guide rails 1003 bear the load synchronously, avoiding localized wear caused by uneven force distribution in traditional mechanical guide rails and extending the life of the guide rails.

[0087] This design achieves synergistic optimization of high-precision positioning, high-rigidity support, and motion stability through the combination of V-shaped recessed guide rail 1002 and flat guide rail 1003 and uniformly distributed oil supply unit 3000.

[0088] In some embodiments of this application, the drive-type hydrostatic guideway assembly further includes a cable chain 8000, one end of which is connected to the bed 1000, and the other end of which is connected to the worktable 2000; the hydrostatic oil line 6021 is disposed on the cable chain 8000. The cable chain 8000 is typically arranged on the side or bottom of the bed 1000, parallel to the length direction of the hydrostatic guideway 1001, to avoid interfering with the movement of the worktable 2000. One end of the cable chain 8000 is fixed to the fixed end bracket of the bed 1000 by bolts or a pressure plate, and the other end is connected to the side of the worktable 2000 by a movable bracket to ensure synchronous movement with the worktable 2000.

[0089] The bending radius of the cable chain 8000 must meet the minimum bending radius requirement of the hydrostatic oil pipe to avoid obstructing oil flow. The hydrostatic oil supply pipe, return pipe, and control oil pipes (such as pressure sensor wiring) are integrated inside the cable chain 8000, with each pipe secured by separators or clips to prevent mutual friction. The cable chain 8000 provides mechanical protection for the hydrostatic oil pipe 6021, preventing contamination or damage from chips, coolant, dust, etc., thus extending the pipe's lifespan. The regular bending motion of the cable chain 8000 reduces the risk of fatigue fracture caused by random pipe swaying, especially effective in high-frequency reciprocating motion scenarios. The cable chain 8000 constrains the pipe's movement trajectory, eliminating interference from pipe swaying on the worktable 2000 and improving motion stability.

[0090] In some embodiments of this application, an integrated pressure sensing system is also included, comprising a first pressure sensor 7000 and a second pressure sensor 7001 connected to the aforementioned oil circuit system 6000; the first pressure sensor 7000 is disposed within the oil film cavity formed by the V-shaped recessed guide rail 1002 and the worktable 2000. The second pressure sensor 7001 is disposed within the oil film cavity formed by the planar guide rail 1003 and the worktable 2000.

[0091] In the two inclined oil film cavities of the V-shaped recessed guide rail 1002, first pressure sensors 7000 are arranged at intervals along the length of the guide rail to monitor the lateral oil film pressure. In the oil film cavity of the planar guide rail 1003, second pressure sensors 7001 are distributed in a matrix, covering the entire length and width of the guide rail, focusing on monitoring the vertical support pressure.

[0092] The sensor signal line is led out through a dedicated cable tray inside the cable chain 8000 and connected to the external control system. The sensor data is fed back to the pressure regulating valve of the oil circuit system 6000 in real time. When a local pressure deviation is detected to exceed the threshold, the flow rate of the corresponding branch is automatically adjusted to achieve closed-loop control of the oil film pressure.

[0093] The integrated pressure sensing system can directly measure the pressure inside the oil film cavity, accurately reflecting changes in oil film thickness and stiffness. Furthermore, during machining, when the workpiece weight distribution is uneven or the cutting force changes abruptly, the system adjusts the flow rate of each oil supply unit in real time based on pressure feedback to maintain constant oil film stiffness.

[0094] This integrated pressure sensing system enables real-time status perception, adaptive control, and predictive maintenance of the hydrostatic guide rail 1001 by precisely arranging sensors within the oil film cavity of the V-shaped and planar guide rails 1003.

[0095] In some embodiments of this application, reference is made to Figures 6-9 , Figure 6 This is a partial connection diagram of the oil circuit system provided in the embodiments of this application. Figure 7 This is a schematic diagram showing the connection between the third flow control valve and the static pressure guide rail provided in the embodiments of this application. Figure 8 This is a top view of the drive hydrostatic guide rail assembly hidden behind the worktable, as provided in the embodiments of this application. Figure 9 for Figure 7 A partial enlarged view at point A. The oil circuit system 6000 shown is also equipped with a flow control valve and a static pressure valve 6033: a first flow control valve 6030 is configured between the first oil tank 6010 and the first oil inlet 4001; a second flow control valve 6031 is configured between the first oil tank 6010 and the second oil inlet 5001; a third flow control valve 6032 and a static pressure valve 6033 are configured between the second oil tank 6020 and the oil supply unit 3000.

[0096] The first flow control valve 6030 is installed in the middle of the connecting pipeline between the first oil tank 6010 and the first oil inlet 4001 of the first one-way cylinder 4000, and the second flow control valve 6031 is installed in the middle of the connecting pipeline between the first oil tank 6010 and the second oil inlet 5001 of the second one-way cylinder 5000, to ensure that it can directly control the flow rate of oil entering the cylinder.

[0097] Specifically, either an electromagnetic proportional flow valve or a manually adjustable flow valve can be selected. The electromagnetic proportional flow valve controls the opening degree through an electrical signal, achieving precise automatic adjustment of the flow rate; the manually adjustable flow valve is mechanically adjusted via a knob or handwheel, and is suitable for use during the commissioning phase.

[0098] On the connecting pipeline between the second oil tank 6020 and the oil supply unit 3000, the third flow control valve 6032 is installed close to the second oil tank 6020 to initially adjust the total flow; the static pressure valve 6033 is installed close to the oil supply unit 3000 to finely control the static pressure and flow of the oil entering the oil film chamber.

[0099] The third flow control valve 6032 is an adjustable throttle valve, which controls the total flow into the oil supply unit 3000 by adjusting the size of the opening; the static pressure valve 6033 is a pressure-compensated flow valve, which automatically adjusts the opening according to the pressure feedback of the oil film chamber to ensure that the pressure in the oil film chamber is stable and is not affected by system pressure fluctuations.

[0100] The first and second flow control valves independently regulate the flow rate of oil entering the dual cylinders, allowing the extension and retraction speeds of the first and second unidirectional cylinders to be flexibly adjusted according to actual working conditions. This ensures speed matching when the dual cylinders are linked in reverse, eliminates mechanical shock caused by speed differences, and improves motion stability and displacement accuracy.

[0101] The third flow control valve 6032 works in conjunction with the static pressure valve 6033 to ensure a stable flow of static oil entering the oil film chamber, maintain uniform oil film thickness, and improve the load-bearing capacity and vibration resistance of the worktable 2000. The pressure compensation function of the static pressure valve 6033 can automatically adjust the flow rate when the system load changes, keeping the oil film pressure fluctuation range to a minimum and ensuring the stability of the worktable 2000 in a suspended state.

[0102] The combination of the flow control valve and the static pressure valve 6033 enables the system to adapt to the flow and pressure requirements under different working conditions, such as automatically increasing the oil supply flow during heavy-duty processing and reducing energy consumption during no-load operation.

[0103] When abnormal pressure or flow fluctuations occur in the system, the flow control valve can cut off or adjust the oil circuit in time, and the static pressure valve 6033 can maintain the basic pressure of the oil film chamber, preventing the worktable 2000 from directly contacting the bed 1000, thus protecting the equipment and improving the safety of system operation.

[0104] The bidirectional symmetrical oil circuit layout, with dual cylinders employing symmetrical oil supply pipelines and valve group designs, shortens oil response time, reduces pressure fluctuations, ensures consistent thrust during the forward and reverse movements of the 2000-degree worktable, and avoids uneven load deformation caused by unilateral drive. Under normal conditions, it relies on non-contact hydrostatic lubrication, with the dual cylinders only bearing the driving force rather than supporting the load, significantly reducing mechanical wear and extending the life of components (such as cylinder seals).

[0105] In some embodiments of this application, the second oil tank 6020 is connected to each oil supply unit 3000 via a rigid distribution pipe. That is, the static pressure oil output from the second oil tank 6020 is distributed to each oil supply unit 3000 via the rigid distribution pipe, thereby providing pressurized oil to the oil film cavity between the static pressure guide rail 1001 and the worktable 2000. The rigid distribution pipes are arranged in a tree-like or ring-like pattern with the second oil tank 6020 as the center. A main rigid distribution pipe is led out from the oil tank, and then, according to the distribution of the oil supply units 3000, branches are formed by using tee and cross fittings, connecting to the connecting oil port 3002 of each oil supply unit 3000. The rigid distribution pipes are fixedly installed along the bed 1000 or the equipment frame, and the pipeline is kept stable by supports, pipe clamps, and other components to prevent pipeline swaying from affecting oil delivery.

[0106] Rigid manifolds are less prone to deformation, maintaining a stable pipeline shape during oil delivery and preventing pressure fluctuations caused by elastic deformation. Compared to flexible hoses, rigid manifolds result in less oil pressure loss, ensuring stable and uniform pressure oil for each oil supply unit 3000, maintaining constant oil film chamber pressure, and improving the operational stability and accuracy of the worktable 2000.

[0107] A grinding machine includes the aforementioned driven hydrostatic guideway assembly. Other structures of the grinding machine and its assembly and connection with the driven hydrostatic guideway assembly are available in the prior art.

[0108] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0109] The above embodiments are merely illustrative of several implementation methods of this application, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the patent application. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this application, and these all fall within the protection scope of this application. Therefore, the protection scope of this patent application should be determined by the appended claims.

Claims

1. A drive-type hydrostatic guide rail assembly, characterized in that, The drive-type hydrostatic guide rail assembly includes: The bed (1000) has a hydrostatic guide rail (1001) on its surface. The worktable (2000) is mounted on the hydrostatic guide rail (1001) and has an oil film cavity between it and the hydrostatic guide rail (1001); An oil supply unit (3000) is disposed on the hydrostatic guide rail (1001) and is used to fill the oil film cavity with hydrostatic oil. The first one-way hydraulic cylinder (4000) is disposed on the surface of the bed (1000) and parallel to the length direction of the hydrostatic guide rail (1001); The second one-way cylinder (5000) is disposed on the surface of the bed (1000), parallel to the length direction of the hydrostatic guide rail (1001), and opposite to the orientation direction of the first one-way cylinder (4000); the first piston rod of the first one-way cylinder (4000) and the second piston rod of the second one-way cylinder (5000) are both connected to the worktable (2000); The oil circuit system (6000) is connected to the first one-way cylinder (4000), the second one-way cylinder (5000) and the oil supply unit (3000) respectively.

2. The drive-type hydrostatic guide rail assembly according to claim 1, characterized in that, The oil circuit system (6000) includes a first oil tank (6010) and a reversing valve (6011); The first one-way cylinder (4000) includes a first oil inlet (4001) and a first oil return port (4002) communicating with the first oil tank (6010). When hydraulic oil is filled into the first oil inlet (4001), the first piston rod extends relative to the first one-way cylinder (4000). The second one-way cylinder (5000) includes a second oil inlet (5001) and a second oil return port (5002) communicating with the first oil tank (6010). When hydraulic oil is filled into the second oil inlet (5001), the second piston rod extends relative to the second one-way cylinder (5000). The reversing valve (6011) is configured on the common communication passage between the first oil inlet (4001) and the second oil inlet (5001) and the first oil tank (6010).

3. The drive-type hydrostatic guide rail assembly according to claim 2, characterized in that, The oil circuit system (6000) includes a second oil tank (6020) and a static pressure oil pipeline (6021), wherein the second oil tank (6020) is connected to all the oil supply units (3000) through the static pressure oil pipeline (6021).

4. The drive-type hydrostatic guide rail assembly according to claim 3, characterized in that, The oil supply unit (3000) is evenly arranged along the length of the hydrostatic guide rail (1001). The oil supply unit (3000) is provided with an oil supply port (3001) facing the oil film cavity and a connecting oil port (3002) for connecting the hydrostatic oil pipeline (6021).

5. The drive-type hydrostatic guide rail assembly according to claim 4, characterized in that, The hydrostatic guide rail (1001) is respectively configured as a V-shaped recessed guide rail (1002) and a flat guide rail (1003). The worktable (2000) is slidably connected to the V-shaped recessed guide rail (1002) and the flat guide rail (1003) simultaneously through a slider set at the bottom. The oil supply unit (3000) is evenly distributed inside the V-shaped recessed guide rail (1002) and the planar guide rail (1003).

6. The drive-type hydrostatic guide rail assembly according to claim 3, characterized in that, Also includes: A cable chain (8000), one end of which is connected to the bed (1000) and the other end of which is connected to the worktable (2000). The hydrostatic oil line (6021) is configured on the drag chain (8000).

7. The drive-type hydrostatic guide rail assembly according to claim 5, characterized in that, It also includes an integrated pressure sensing system, which includes a first pressure sensor (7000) and a second pressure sensor (7001) connected to the oil circuit system (6000). The first pressure sensor (7000) is disposed in the oil film cavity formed by the V-shaped recessed guide rail (1002) and the worktable (2000); the second pressure sensor (7001) is disposed in the oil film cavity formed by the planar guide rail (1003) and the worktable (2000).

8. The drive-type hydrostatic guide rail assembly according to claim 3, characterized in that, A first flow control valve (6030) is provided between the first oil tank (6010) and the first oil inlet (4001). A second flow control valve (6031) is provided between the first oil tank (6010) and the second oil inlet (5001). A third flow control valve (6032) and a static pressure valve (6033) are provided between the second oil tank (6020) and the oil supply unit (3000).

9. The drive-type hydrostatic guide rail assembly according to claim 3, characterized in that, The second oil tank (6020) is connected to each of the oil supply units (3000) through a rigid diversion pipe.

10. A grinding machine, characterized in that, The drive-type hydrostatic guide rail assembly includes any one of claims 1-9.

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